Control valve for hydraulic systems



Oct. ll, 1949- G. BRINKMANN 2,484,373 CONTROL VALVE FOR HYDRAULIC SYSTEMS Filed Oct. ll, 1943 2 Sheets-Sheet l SUMP ` I N V EN TOR. GUE/v THE/F 5mm/@NN /7 TTU/@VE Y Oct. 11, 1949. G. BRINKMANN 2,484,373

CONTROL VALVE lFOR HYDRAULIC SYSTEMS l N VEN TOR. Gum//mP/A//WANN Afro/PNE? Patented Oct. 11, 1949 coNraoL'vALvEL-ro HYDRAULIC' SYSTEMS C Guenther Brinkmann; Detroit, Mich.,.-assignor\ to F1lin-.(elL-O:.(loiporaition, Detroit, Mich., a. corporatiorroMichigan Application October 11, 1943,: Serial N0."505',796

4 Claims. (Cl. 137-153) A"Ifhisf invention relates to: a` control w valve .and moreI` particularlyl f to f a` control valve `for` use in af system'fincludingfhranched hydraulic circuits. Thefunctions'of such aavalve are' the `protection (af-such a' system against'excess fpressureand machines @which f may 4be :associated therewith, against hazards incident todeiiciencies of =pres sure in` zthe lsystem.

In; the operation ofl hydrainical-ly'idriven machines-,f Suche as machine tools Vhaving 1 a r multiplicityY 'of fluidfactuated mechanismsy powered from avcommonsou-rce offluid pressure, there aretin'stances where an -excessive reduction fin pressure or ai failure' thereofrmight cause injury to the operator, the machine, or the Work.

Such a conditionmay1be lillustratedby a grinding.v machine wherein af work` table having a'fworlr holding chuck`mountedthereon isarranged to have1 the table: reciprocated and thez'work` chuck closedr respectively by i branch:A circuits i cfr the: as-

sociatedhydraulic system. In such case,l thezwork is presentedforf'cuttinglby a: grinding awheel which usually 'is Ldrivenbyfa separate sourceA of power, such'. as antelectric motor.

."Heretofore in such. machinesyonefbranch: of the associated'rhydraulicsystemfhas been utilized to operatethe `.Work holding :chuck and-another branchl -of *the system, withoutf' safety controls, has been Lutilized 'tof'iurnishf power to the table reciprocatinge means.

Underthe lformer conditioniitis seen to bespossible that, `upon excessive reduction of'. hydraulic pressure `in the system, the grip 1ct. the' work holding chuci: on y the workpiece Vmay :become insecure before movement of the vtable will cease. Insuch anlevent the Yforcesimposedlay thegrinding Wheel upon the workpieceanay be suiTlcient-fto tear. :the latten from .the chuck, endangering.- the opera-tor, themachine and the workpiece.

V.The dangerous. condition illustrated may :be completelyV avoided or substantially reduced r if, uponu excessive reduc-tion .fofwpressure the hydraulic -system,. the fluid supplied for actuation either-table traverseriscut off betere the pressure suppliedfor closing the worin-holdingchuclr has dropped to. a point. where .fail-ure.- of itssgripupon the workpiece is imminent.

.Cessation of wiiuid supply .tothe table` recipro- CatingmeanshastWoeffects which-tend. to pre-` vent rfailure. of the. chuck.. to hold the workpiece. First, the. discontinuance of-4 tablev .traverse ceases torpresent. additional .work stock for` removalf'by theA grinding. .wheelthus reducing the forces which must.. he. resisted .bythe `work... chuck. Secondly,

,-2 iiuid from the system occasioned by stoppageof movement of .ther mach-iney tableI frequently-enables the' source ofzipressureauid to Amaintain sufficient .pressure upon' the i work chuck tto'- avoid failure of its holding force.

It is, therefore, r.an-object -of :my inventionto provide a valvev vfor controlling the pressure in asystem of branched :circuits inI such -amanner that' 'a' predetermined maximum of i pressure f is not permitted to 'be Iexceeded in any of said branches.

vAnother objectfofl thelinvention-:is tof provide a valve structureawhichwill cut offthe` supply of fluid Pto certain of said'system'rbranchesl upon occurrence' of a" pressure supply* to* saidA system Whichfis'less thanv afpredetermined minimum.

A'fur'ther object of my invention is to'rprovide aunitary controlrvalve structurer'whch will limit the maximum pressure in--asysternfof"branched circuits to-zaipredetermined `valueV and 'to :interrupt the supply of fluid to certain ofsaid'branches when fluid isfsuppliedto'thefsystem at less'tha-n such value.

"A still iurtherobjectis to providefafvalve structure of simple,'^reliablei andv inexpensive lconstruction rin-` `which the `control f functions previously mentioned: are accomplishedfby y.a single A valve member-r-re'ciprocable inai valve casing.

In the drawings:

Figxzl is a schematic representation of my-.fim-

proved control valvev in association-with a source of uid under pressure, a plurality .or` hydraulic circuit branches and a; grinding. machine.

"Fig 2: isa front 'elevational viewef lmy control valve.

Fig-3 lisfa. top -planviewlooking on Fig. 2.

'Figui is a bottomfplan viewloolring` onY Fig. 2.

vFigui isa right elevation on facet-,5 oiEiggZ;

'Figf 6 is a left elevation on facet-610i Fig.r2.

Fig. 8 isa horizont-,a1` section on --.of Fig.r7.

Referring particularly to Fig.. 1, myimp-roved control valvefgenerally indicatedl bythe numeral .i043 is 'shown'in one Aillustrative Yenvironment wherein fluid under. pressure is .delivered thereto from' a. 'supply' tank H32 through pump suction conduit lli-4.,v by' iiuid'A pressure pump I uti lwhich may beof a-widefvariety of commonly knownconstru-ations. Pump m6 dischargestinto:branched conduit |88, one'lora-nch thereof delivering fluidJ to the valve E08 yandv another, through'a valve l I8, is adapted "to admit fluid pressure vto a'work holding chuckf I l2to cause said chuck,rwhich may-be of any of `thev Well-known constructions, to` v grip the very-.actof reducing the ...draft lof. hydraulic 55. theywork W. vWhen val-ve Hit is` turned toan alternative position, connection between pressure conduit |08 and conduit I|4 is closed and the pressure in the Chuck H2 and conduit I|4 is relieved to branched exhaust conduit I I6.

In the present instance, work chuck l I2 is shown mounted upon a machine table ||8 which is reciprocable upon a machine base (not shown) by a conventional actuator |20 whereby the work may be presented in cutting relation to a conventional grinding wheel head |22 which is here represented as being driven by electric motor means. This may be of any suitable construction and mounted on an infeed cross slide (not shown) or other portion of the machine in any suitable manner.

A manually operable valve |24 is adapted to control admission of pressure uid from valve through `conduit |26 to either end of actuator |20 through associated conduits |20-a, or |20-b to cause it to move in either direction or to be stopped at will. The exhaust fluid discharged from actuator |20 is returned to the supply tank through exhaust conduit ||6. It will be under stood that valve |24 may be actuated manually -or y automatically in any desired manner.

Through controlled ports and passages within the structure |00 which will later be described in detail, conduit |08 is connected with relief conduit |28 through a suitably variable restriction, bypassing to reservoir |02 that portion of the fluid displaced by pump |06 which is necessary to prevent the application of excessive pressures to the associated hydraulic system.

So long as the pressures applied upon conduit |08 lie within a normal range, continuous communication is maintained between conduit |08 and conduit |26 through valve |00. However, when the pressure applied on conduit |08 drops below a value which might render uncertain the ability of chuck ||2 to hold the work W under any forces which might normally be appli-ed thereto, the valve |00 interrupts the said cornmunication and'actuator |20 is rendered incapable of moving its associated machine table I I8 regardless of the position of valve I 24,

Referring to Figs. 2 through 8, the valve |00 is seen to include a body part 2 which is provided with a central bore 4, closed at the bottom end by a screw held cap 6. Throughout the upper end of body' part 2, the bore 4 is enlarged to form a H spring housing I0 closed at its upper end by cap I2. Housing I0 has a boss I5 traversed by a tapped opening I4 for receiving a, return conduit |28 through which bypassed fluid is returned to the hydraulic sump or fluid supply tank,

Alongl the length of bore 4 are three spaced annular port enlargements I6, I8, and 20. Through branched passage 22, formed in body part 2, ports I6 and I8 are in constant communication with each other and with iiuid pressure inlet 24 which is connected by branched conduit |08 to receive fluid under pressure from the fluid supply pump |06. Passage 22 also is in constant communication through a restricted snubber passage 24-a with the lower end of bore 4 and applies the pressure of pump |06l beneath the lower face of piston valve assembly 26. Port 20 is in constant communication with 28 which last is in constant communication with the conduit |26 of the circuit which is to have its fluid supply discontinued upon excessive pressure reduction in conduit |08. The piston Valve assembly 26 includes a closely tted piston valve member 28 slidable in bore 4, a lower ycap and plug member 30 which xedly closes a lower axial bore 32 in the piston 29 and a spring hanger 34 which rests and abuts upon the piston valve assembly 26 or upon shims or spacing washers which may be placed therebetween to predetermine the force which will be exerted on the assembly 26 by the spring 36. The lower end of the spring 36 bears upon hanger 34. The upper end of this spring is restrained by cap I2. The hanger 34 is formed with a central aperture which registers with an upper axial bore 38 in piston 29 continuously connecting upper bore 38 with spring housing I0, return passage I4, and return conduit |28.

The section Fig. 8 shows the lower axial bore 32 pierced by cross bores 44 and is typical of respective sections through Valve 29 including cross bores 40 and 46.

It may now be seen that when the force of the spring 36 takes preponderance over the upwardly acting pressure applied on the lower face of valve assembly 26, the spring will hold the valve in its lowermost position severing communication between port I6 and cross holes 40. When the pressure of the pump |06 (or other source) applied through conduit |03, inlet 24, passages 22 and 24-a upon the lower face of valve assembly 26 takes the predominance, the valve will move upwardly against the resistance of spring 36 bringing port I6 into communication with cross bores 40, bore 38, housing I0, and exit passage I4 into return conduit |28. The pressure thus applied on assembly 26 will so govern the area of the communication that the maximum pressure generated by pump |06 will be limited to a predetermined value even though there be no other escape for fluid displaced by the pump.

In the lowermost position of valve 26, the top edge of cross holes 44 will be below the lower edge of port I8 and there will be no communication therebetween. However, in the rise of valve 26 from its lowermost position, communication at the last named point will be established before communication between port I6 and cross holes 40 is established. This means that, at some point in a progressive rise of pump pressure from Zero to the pressure at which valve 26 begins to perform its bypassing function, a pressure is reached at which communication is established between inlet 24 and port 28 through passages 22, port I8, cross holes 44, bore 32, cross holes 46, port 20, and connection 28 to conduit |26. At all pump pressures above this value, fluid from the pump |06 may be discharged from outlet 28 into conduit |26, at all pressures below this value, the existing pressure of pump |06 is applied on conduit |08 but is cut off from conduit |26.

For illustrative purposes, let it now be considered that the normal working pressure of the pump |06 as determined by the valve |06, is 250 pounds per square inch and the holding force of the chuck |I2 is acceptably safe at a minimum working pressure of |25 pounds per square inch. My control valve may then be constructed and adjusted to limit the maximum working pressure iu conduits 08 and |26 to 250 pounds per square inch. If for any reason the pressure applied to conduit |00 drops below 125 pounds per square inch, the communication between conduits |08 and |26 made through valve |00 of Fig. 1 is severed and movement can no longer be given to table A regardless of the position of valve |24.

While my improved control valve has been illustratively shown in one of its simpler embodiments, it is susceptible to various modications diierent uses. It is, therefore, my intention that the scope of the invention shall be limited only by the appended claims.

I claim as my invention:

1. A valve mechanism comprising, in combination, a casing having a valve bore opening at one end to a pressure chamber and at the other end to an open spring chamber, and formed with two axially-spaced iixed inlet ports and an outlet port opening to the periphery of said bore, said inlet ports being connected to said pressure chamber and adapted for connection to a source of pressure fluid, a valve member reciprocable in said bore and formed with an axial by-pass bore opening to said spring chamber and with a by-pass valve port opening from the periphery of said member to said axial bore for movement into and out of communication with one of said inlet ports, spring means disposed in said spring chamber and acting on said valve member to urge said member toward a closed position, said valve member being formed with a second axial bore in constant communication with said outlet port and with an inlet valve port opeing from the periphery of said member to said second bore for movement into and out of communication With the other of said inlet ports, said Valve ports being spaced more closely than said inlet ports.

2. A valve mechanism comprising, in combination, a valve housing having a longitudinal valve bore opening at one end to a closed pressure chamber and at the other end to an enlarged `exhaust chamber, said body being formed with an exhaust passage opening from said exhaust chamber, a fluid supply passage connected through a restricted snubber passage to said pressure chamber and opening in parallel to the periphery of said bore respectively through two axially-spaced by--pass and inlet grooves, and a pressure uid discharge passage opening from the periphery of said bore through a relatively Wide annular outlet groove at one side of the said first mentioned grooves, a single valve member slidable in said bore and projecting into said exhaust chamber, a coiled compression spring in said exhaust chamber and acting on said valve member in a direction to close the valve against the oppositely acting force of pressure iiuid in said pressure chamber, said valve member being formed in one 4end portion with a set of radial relief ports movable into and out of communication with said by-pass groove and communicating with an axial bore opening to said exhaust chamber, and being formed in the other end portion with two sets of axially spaced inlet and outlet ports opening to an axial connecting bore closed from said pressure chamber, said outlet ports -being in constant communication With said outlet groove and said inlet ports being movable into and out of communication with said inlet groove, said relief and inlet ports being more closely spaced than said by-pass and inlet grooves and being so located that in the opening movement of said valve member, said inlet ports Will move into communication with said inlet groove before said relief ports are moved into communication with said by-pass groove.

3. A valve mechanism comprising, in combination, a valve housing having a longitudinal valve -bore opening at one end to a closed pressure chamber and at the other end to an open exhaust chamber, said body being formed with a fluid supply passage connected through a restricted snubber passage to said pressure chamber and opening in parallel vto the periphery of said bore respectively through two fixed @axially-spaced by-pass and supply ports, and a pressure iiuid discharge passage opening from the periphery of said bore through a fixed discharge port, an integral valve rmember slidable in said bore and projecting into said exhaust chamber, a coiled coin-pression spring acting on said valve member in a direction to close the Valve against the oppositely acting force of pressure uid in said pressure chamber, said valve member being formed in one end portion with a relief valve port movable into and out of communication with said by-pass port and communicating with a longitudinal passage open to said exhaust chamber, and being formed in the other end portion respectively with axially-spaced inlet and outlet valve ports in intercommunication through a longitudinal connecting passage, said outlet valve port being in constant communication with said discharge port and said inlet valve port being movable into and out of communication with said supply port, said lrelief and inlet valve ports 'being more closely spaced than said by-pass and supply ports and being so located that in the opening movements of said valve member said inlet valve port will move into communication with said supply port before said relief port is moved into communication with said lby-pass port.

4. A valve mechanism comprising, in combination, a valve housing having exhaust and discharge outlets and having a longitudinal valve bore opening at one end to a closed pressure chamber, said body being formed with a supply inlet connected to said pressure chamber and opening in parallel to the periphery of said bore respectively through two axially-spaced by-pass and supply ports, a single valve member slidable in said bore, a coiled compression spring acting on said valve member in a direction to close the valve against the oppositely acting force of pressure fluid in said pressure chamber, said valve member being formed in one end portion with a relief port in constant communication with said exhaust outlet and movable into and out of communication with said by-pass port, and being formed in the other end portion respectively With axially spaced intercommunicating inlet and outlet ports, said outlet port being in constant communication with said discharge outlet and said inlet port being movable into and out of communication with said supply port, said relief and inlet ports being more closely spaced than said by-pass and supply ports and being so located that in the opening movements of said valve member said inlet port Will move into communication with said supply port before said relief port is moved into communication with said by-pass port.

GUENTHER BRINKMANN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,655,173 Webber Jan. 3, 1928 1,999,697 Kleckner A-pr. 30, 1935 1,999,698 Kleckner Apr. 30, 1935 2,059,457 Horton Nov. 3, 1936 2,104,390 Murphy Jan. 4, 1938 2,118,779 Rippl May 24, 1938 2,154,038 Evrell Apr. 11, 1939 2,167,328 Beggs July 25, 1939 

